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EP4027018A1 - Pale de ventilateur à flux transversal, ventilateur à flux transversal et unité intérieure de climatiseur - Google Patents

Pale de ventilateur à flux transversal, ventilateur à flux transversal et unité intérieure de climatiseur Download PDF

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Publication number
EP4027018A1
EP4027018A1 EP20870951.9A EP20870951A EP4027018A1 EP 4027018 A1 EP4027018 A1 EP 4027018A1 EP 20870951 A EP20870951 A EP 20870951A EP 4027018 A1 EP4027018 A1 EP 4027018A1
Authority
EP
European Patent Office
Prior art keywords
cross flow
flow fan
blade
pressure face
inner edge
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP20870951.9A
Other languages
German (de)
English (en)
Other versions
EP4027018A4 (fr
Inventor
Hironobu Teraoka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP4027018A1 publication Critical patent/EP4027018A1/fr
Publication of EP4027018A4 publication Critical patent/EP4027018A4/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0025—Cross-flow or tangential fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/301—Cross-sectional characteristics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0071—Indoor units, e.g. fan coil units with means for purifying supplied air
    • F24F1/0073—Indoor units, e.g. fan coil units with means for purifying supplied air characterised by the mounting or arrangement of filters

Definitions

  • the present disclosure relates to a cross flow fan blade, a cross flow fan, and an air conditioner indoor unit.
  • a cross flow fan In, for example, air conditioner indoor units, in order to blow air, a cross flow fan is often used.
  • a cross-sectional shape of a cross flow fan blade a pressure face and a negative pressure face on a side opposite to the pressure face are curved in a fan rotation direction toward an outer side of the blade from a fan rotary shaft. That is, the cross flow fan blade has a bow shape in which a central portion of the blade is disposed away from a straight line connecting an inner edge and an outer edge of the blade.
  • PTL 1 discloses a method of, in order to increase energy efficiency of a cross flow fan, reducing loss by suppressing separation of a flow at a negative pressure face as a result of setting a maximum thickness position of a blade closer to an inner edge than to an outer edge.
  • An object of the present disclosure is to provide a cross flow fan blade that is capable of increasing energy efficiency of a cross flow fan.
  • a first aspect of the present disclosure is a cross flow fan blade including an inner edge (42) disposed on an inner circumferential side of a cross flow fan (10); an outer edge (43) disposed on an outer circumferential side of the cross flow fan (10); and a base part (41) formed between the inner edge (42) and the outer edge (43), and having a pressure face (41p) and a negative pressure face (41n).
  • a thickness of the inner edge (42) is larger than a thickness of the outer edge (43).
  • a maximum thickness position of the base part (41) is set closer to the inner edge (42) than to the outer edge (43).
  • a second aspect of the present disclosure is the cross flow fan blade according to the first aspect, in which 0.054 ⁇ tmax/L is satisfied.
  • a third aspect of the present disclosure is the cross flow fan blade according to the first aspect or the second aspect, in which 0.074 ⁇ tmax/L ⁇ 0.086 is satisfied.
  • a fourth aspect of the present disclosure is the cross flow fan blade according to any one of the first aspect to the third aspect, in which the maximum thickness position of the base part (41) is set in a range of 5% to 45% of the blade chord length from an end of the inner edge (42).
  • a fifth aspect of the present disclosure is the cross flow fan blade according to any one of the first aspect to the fourth aspect, in which an inlet angle of the inner edge (42) is set to be greater than or equal to 80° and less than or equal to 90°.
  • a sixth aspect of the present disclosure is the cross flow fan blade according to any one of the first aspect to the fifth aspect, in which a surface on a side of the negative pressure face (41n) of at least one of the inner edge (42) and the outer edge (43) is a curved surface that is convex on an outer side, and the curved surface is smoothly connected to the negative pressure face (41n) and is connected to the pressure face (41p) at an angle that is greater than or equal to 85° and less than or equal to 90°.
  • a seventh aspect of the present disclosure is a cross flow fan (10) including a plurality of the blades (40) according to any one of the first aspect to the sixth aspect, the plurality of blades (40) being arranged around a rotary shaft (22).
  • the seventh aspect since it is possible to provide a width of a flow path between blades and suppress an increase in flow velocity, it is possible to suppress loss at the blade (40) and to thus increase energy efficiency.
  • An eighth aspect of the present disclosure is the cross flow fan according to the seventh aspect, in which a fan diameter is greater than or equal to 126 mm.
  • the eighth aspect compared with a small-diameter cross flow fan having a fan diameter that is less than 126 mm, it is possible to considerably reduce the thickness of the blade, and thus the effect of reducing weight and material costs is also increased.
  • a ninth aspect of the present disclosure is an air conditioner indoor unit (1) including the cross flow fan (10) according to the seventh aspect or the eighth aspect.
  • Fig. 1 is a sectional view of an air conditioner indoor unit (1) according to an embodiment.
  • the air conditioner indoor unit (1) primarily includes a body casing (2), an air filter (3), an indoor heat exchanger (4), a cross flow fan (10), a vertical flap (5), and a horizontal flap (6).
  • "R1" and “R2” denote a suction region and a blow-out region of the cross flow fan (10), respectively.
  • a top surface of the body casing (2) has a suction port (2a).
  • the air filter (3) facing the suction port (2a) is disposed on a downstream side of the suction port (2a).
  • the indoor heat exchanger (4) is disposed further on a downstream side of the air filter (3).
  • the indoor heat exchanger (4) is constituted by coupling a front-side heat exchanger (4a) and a rear-side heat exchanger (4b) so as to form an inverted V shape in side view.
  • the front-side heat exchanger (4a) and the rear-side heat exchanger (4b) are each constituted by arranging a large number of plate fins side by side in parallel and mounting the plate fins on heat transfer tubes.
  • the cross flow fan (10) having a substantially cylindrical shape and having a fan diameter D is provided on a downstream side of the indoor heat exchanger (4) so as to extend in a width direction of the air conditioner indoor unit (1) (direction perpendicular to the sheet plane of Fig. 1 ).
  • the cross flow fan (10) is disposed parallel to the indoor heat exchanger (4).
  • the cross flow fan (10) includes an impeller (20) that is disposed so as to be interposed between portions of the inverted V-shaped indoor heat exchanger (4), and a fan motor (not shown) for driving the impeller (20).
  • the cross flow fan (10) as a result of rotating the impeller (20) in the direction of arrow A1 in Fig.
  • the cross flow fan (10) is a transverse fan at which an airflow traverses the cross flow fan (10).
  • the blow-out port (2b) is provided in a bottom surface of the body casing (2).
  • a rear side of a blow-out passage that communicates with the blow-out port (2b) situated downstream from the cross flow fan (10) is constituted by a scroll member (2c).
  • a lower end of the scroll member (2c) is connected to a rear edge of the blow-out port (2b).
  • a guide surface of the scroll member (2c) has a smooth curved shape having a curvature center on a side of the cross flow fan (10) in sectional view.
  • a tongue part (2d) is provided on a front side of the cross flow fan (10), and an upper side of the blow-out passage that continues from the tongue part (2d) is coupled to a front edge of the blow-out port (2b).
  • the direction of an airflow that is blown out from the blow-out port (2b) is adjusted by the vertical flap (5) and the horizontal flap (6).
  • Fig. 2 is a perspective view of the impeller (20) of the cross flow fan (10).
  • the impeller (20) has a structure in which a plurality of fan blocks (30) (for example, seven fan blocks (30)) are joined to each other in series, and two ends of the structure are provided with a corresponding one of end plates (21) and (24).
  • the impeller (20) has a metallic rotary shaft (22) on an axis (O). An end portion of the rotary shaft (22) protrudes from the end plate (21) disposed at one end of the impeller (20), and the end portion is supported by the body casing (2).
  • a motor (not shown) that drives the rotary shaft (22) is provided on a side of the end plate (24) disposed on the other end of the impeller (20).
  • Each fan block (30) includes a plurality of blades (40) and a ring-shaped supporting plate (50).
  • the plurality of blades (40) are arranged around the rotary shaft (22) with the rotary shaft (22) being a center. Adjacent blades (40) are spaced apart from each other by a predetermined interval. Two ends of each blade (40) (two ends in a direction in which the rotary shaft (22) extends) are supported by two supporting plates (50), or by a supporting plate (50) and the end plate (21) or the end plate (24).
  • Fig. 3 is a sectional view of blades (40) of the cross flow fan (10) (sectional view in which the blades (40) have been cut by a plane parallel to a supporting plate (50)).
  • the ring-shaped supporting plate (50) has an inner circumferential end (51) that is situated on an inner circumferential side of the cross flow fan (10) and an outer circumferential end (52) that is situated on an outer circumferential side of the cross flow fan (10).
  • All the blades (40) that are disposed in one fan block (30) are disposed so as to contact one inscribed circle (IL) and one circumscribed circle (OL), which are concentric with the inner circumferential end (51) and the outer circumferential end (52).
  • Each blade (40) includes an inner edge (42) disposed on the inner circumferential side of the cross flow fan (10), an outer edge (43) disposed on the outer circumferential side of the cross flow fan (10), and a base part (41) formed between the inner edge (42) and the outer edge (43).
  • Each inner edge (42) is formed so as to have an arc shape that is convex toward the inner circumferential end (51), and contacts the inscribed circle (IL).
  • Each outer edge (43) is formed so as to have an arc shape that is convex toward the outer circumferential end (52), and contacts the circumscribed circle (OL).
  • Each base part (41) has a pressure face (41p) that generates positive pressure on a side in the direction of arrow A1 (hereunder referred to as a "fan rotation direction"), and a negative pressure face (41n) that generates a negative pressure on a side opposite to the side in the fan rotation direction.
  • Each blade (40) is a forwardly facing vane that is curved in the fan rotation direction toward the outer circumferential end (52). Specifically, each blade (40) is inclined by an angle ⁇ with respect to a line (RL) orthogonal to the axis (O) of the cross flow fan (10) and extending radially toward the outer circumference from the axis (O).
  • the inclination ⁇ of each blade (40) is defined as an angle between the radially extending line (RL) and a tangential line (TL) that touches the inner edge (42) and the outer edge (43) of the corresponding blade (40).
  • the pressure face (41p) and the negative pressure face (41n) of each blade (40) are curved in an arc toward the side opposite to the fan rotation direction. In other words, even a curvature center of the arc of each pressure face (41p) and a curvature center of the arc of each negative pressure face (41n) are positioned on the side in the fan rotation direction.
  • a blade chord length L of each blade (40) is a length from an end of the inner edge (42) to an end of the outer edge (43). Specifically, when the tangential line (TL) of each blade (40) is extended toward each of the inner circumferential side and the outer circumferential side, and when a perpendicular line (PL1) that extends upright at the tangential line (TL) and that contacts the inner edge (42) and a perpendicular line (PL2) that extends upright at the tangential line (TL) and that contacts the outer edge (43) are drawn, the length from the perpendicular line (PL1) to the perpendicular line (PL2) is the blade chord length L.
  • the thickness (wall thickness) of the base part (41) that is, the distance between the pressure face (41p) and the negative pressure face (41n) changes gradually from the inner circumferential side toward the outer circumferential side, and a position where the thickness of the base part (41) becomes a maximum (hereunder referred to as a "maximum thickness position") exists.
  • the maximum thickness of each base part (41) is tmax.
  • each base part (41) is defined as the interval between the pressure face (41p) and the negative pressure face (41n) in a direction perpendicular to the pressure face (41p).
  • a maximum thickness position (Lt) is represented by the position of a leg of a perpendicular line drawn to the tangential line (TL) from a portion of a central line (ML) where the thickness becomes the maximum thickness tmax (the central line (ML) being a line obtained by successively joining center points between the pressure face (41p) and the negative pressure face (41n)).
  • the maximum thickness position (Lt) of each base part (41) is set closer to the inner edge (42) (the inner edge end (CLi)) than to the outer edge (43) (the outer edge end (CLo)) on the tangential line (TL).
  • the maximum thickness position (Lt) may be set in a range of 5% to 45% of the blade chord length L from the inner edge end (CLi) on the tangential line (TL).
  • a thickness "ti" of each inner edge (42) is set larger than a thickness "to" of each outer edge (43).
  • ti/to may be ti/to>1.5, or, more desirably, may be ti/to>1.75.
  • Fig. 4 shows the relationship between shaft power and a ratio tmax/L of the maximum thickness tmax of the base part to the blade chord length L in each blade (40) of the cross flow fan (10) of the present embodiment. Note that the magnitude of one division of the vertical axis in Fig. 4 is 0.1 W.
  • the relationship shown in Fig. 4 is a performance evaluation result based on a simulation in a state in which the cross flow fan (10) is installed in the air conditioner indoor unit (1) (wall-mounted indoor unit) of a room air conditioner. Specifically, regarding each ratio tmax/L, the shaft power (power of the rotary shaft (22)) when the number of rotations of the fan is changed and the same air volume is obtained is evaluated. If the air volume is in an air volume range of a general air conditioner indoor unit (for example, 7 to 25 m 3 /min), a relationship that is the same as that in Fig. 4 can be obtained. Note that an input to a motor that rotates the rotary shaft (22) (power consumption) is a value obtained by dividing the shaft power by the motor efficiency, and that, if the shaft power is reduced, the power consumption of the motor is also reduced.
  • the blade shape (cross-sectional shape) of the cross flow fan (10) used in the evaluation in Fig. 4 is as described above. If the number of blades (the number of blades (40) that is provided in one fan block (30)) is the number of blades of a cross flow fan of a general air conditioner indoor unit (for example, 31 to 37), a relationship that is the same as that in Fig. 4 is obtained. Although the evaluation in Fig. 4 is based on a simulation in which blade pitches (intervals between adjacent blades (40)) are equal pitches, even if the blade pitches are unequal pitches applied to a cross flow fan of a general air conditioner indoor unit, a relationship that is the same as that in Fig. 4 can be obtained.
  • each blade (40) of the cross flow fan (10) of the present embodiment it is desirable that tmax/L ⁇ 0.094 be satisfied, more desirable that 0.054 ⁇ tmax/L ⁇ 0.094 be satisfied, and most desirable that 0.074 ⁇ tmax/L ⁇ 0.086 be satisfied.
  • each blade (40) of the cross flow fan (10) of the present embodiment described above when the ratio tmax/L of the maximum thickness tmax of each base part (41) to the blade chord length L is set to be less than or equal to 0.094, it is possible to provide a width of a flow path between blades and suppress an increase in flow velocity.
  • the maximum thickness position (Lt) of each base part (41) close to the inner edge (42) it is possible to suppress separation of a flow at the negative pressure face (41n). Therefore, since loss at each blade (40) can be suppressed, energy efficiency of the cross flow fan (10) is increased.
  • each blade (40) of the cross flow fan (10) of the present embodiment when tmax/L is set to be greater than or equal to 0.054, it is possible to avoid a situation in which, due to the maximum thickness tmax of each base part (41) being made too small, the effect of suppressing separation of a flow at the negative pressure face (41n) is reduced.
  • each blade (40) of the cross flow fan (10) of the present embodiment when tmax/L is set to be greater than or equal to 0.074 and less than or equal to 0.086, it is possible to, while sufficiently providing a width of a flow path between blades and further suppressing an increase in flow velocity, obtain the effect of further suppressing separation of a flow at the negative pressure face (41n).
  • each blade (40) of the cross flow fan (10) of the present embodiment when the maximum thickness position (Lt) of each base part (41) is set in a range of 5% to 45% of the blade chord length L from the end of the inner edge (42) (inner edge end (CLi) in Fig. 3 ), it is possible to further suppress separation of a flow at the negative pressure face (41n) .
  • the thickness "ti" of the inner edge (42) is set larger than the thickness "to" of the outer edge (43). Therefore, since up to the vicinity of the central portion of each blade (40) from the inner edge (42), the thickness of the base part (41) is reduced smoothly, the blade-face curvature of the negative pressure face (41n) is not increased. Consequently, even if a flow is about to be separated on the negative pressure face (41n), since the flow immediately re-adheres to the negative pressure face (41n), it is possible to suppress the separation of the flow up to the central portion of each blade (40) from the inner edge (42).
  • the cross flow fan (10) of the present embodiment in which a plurality of blades (40) are arranged around the rotary shaft (22), since it is possible to provide a width of a flow path between blades and suppress an increase in flow velocity, it is possible to suppress loss at each blade (40) and to thus increase energy efficiency.
  • the fan diameter D is greater than or equal to 126 mm
  • the fan diameter D is greater than or equal to 126 mm
  • the blade chord length L is large compared with that of the small-diameter cross flow fan.
  • the air conditioner indoor unit (1) of the present embodiment including the cross flow fan (10), since energy efficiency of the cross flow fan (10) is increased, it is possible to reduce power consumption.
  • Fig. 5 shows a state of an airflow around the blades (40) of the cross flow fan (10) of the present embodiment, the blades (40) being positioned in the blow-out region R2 (see Fig. 1 ).
  • Fig. 6 shows a state of an airflow around blades (40) of a cross flow fan according to Comparative Example 1, in which tmax/L is set to be greater than 0.094. Note that Fig. 6 also shows the state of the airflow in a blow-out region. Even in Comparative Example 1, a maximum thickness position (Lt) of each base part (41) exists closer to an inner edge (42) than to an outer edge (43), and the blade pitch is the same as that in Fig. 5 .
  • Fig. 7 shows a state of an airflow around blades (40) of a cross flow fan according to Comparative Example 2, in which tmax/L is set to be less than 0.054. Note that Fig. 7 also shows the state of the airflow in a blow-out region. Even in Comparative Example 2, a maximum thickness position (Lt) of each base part (41) exists closer to an inner edge (42) than to an outer edge (43), and the blade pitch is the same as that in Fig. 5 .
  • Fig. 8 is a sectional view of a blade (40) of a cross flow fan (10) according to Modification 1. Note that, in Fig. 8 , structural elements that are the same as those of the embodiment shown in Fig. 3 are given the same reference signs. In Fig. 8 , the external shape of each blade (40) shown in Fig. 3 is shown by a broken line. Fig. 8 shows by arrows a state of an airflow in the vicinity of a negative pressure face (41n) of a blade (40) of the cross flow fan (10) of the present modification, the blade (40) being positioned in the blow-out region R2 (see Fig. 1 ).
  • a feature of the blade (40) of the modification shown in Fig. 8 is that an inlet angle ⁇ of an inner edge (42) is set to be greater than or equal to 80° and less than or equal to 90°, for example, at 86°. That is, a curve of the blade (40) of the present modification is set smaller than a curve of each blade (40) of the embodiment above (the inlet angle ⁇ of the inner edge (42) is, for example, 92.7°).
  • the inlet angle ⁇ of the inner edge (42) is defined as follows.
  • an angle that is formed by a tangential line (SIL) to the inscribed circle (IL) and a tangential line (SML) to the central line (ML) is the inlet angle ⁇ of the inner edge (42).
  • the inlet angle ⁇ of the inner edge (42) is set to be greater than or equal to 80° and less than or equal to 90°, the curve of the blade (40) is small, and thus an airflow moves easily along the negative pressure face (41n) of the blade (40). Therefore, since it is possible to further suppress separation of a flow at the negative pressure face (41n), it is possible to further suppress loss at the blade (40), and to thus further increase energy efficiency of the cross flow fan (10).
  • Fig. 9 is a sectional view of a blade (40) of a cross flow fan (10) according to Modification 2
  • Fig. 10 is a sectional view showing in an enlarged form an outer edge (43) of the blade (40) of the cross flow fan (10) shown in Fig. 9 .
  • structural elements that are the same as those of the embodiment shown in Fig. 3 are given the same reference signs.
  • the external shape of each blade (40) shown in Fig. 3 is shown by a broken line.
  • FIGS. 9 and 10 show by arrows a state of an airflow in the vicinity of a negative pressure face (41n) of the blade (40) of the cross flow fan (10) of the present modification, the blade (40) being positioned in the suction region R1 (see Fig. 1 ).
  • a surface of an outer edge (43) on a side of the negative pressure face (41n) is a curved surface (ws) that is convex on an outer side, and that the curved surface (ws) is smoothly connected to the negative pressure face (41n). That is, a curvature radius of the curved surface (ws) is larger than a curvature radius of the surface of each outer edge (43) of the present embodiment.
  • the curved surface (ws) is connected to a pressure face (41p) at an angle that is greater than or equal to 85° and less than or equal to 90°.
  • the angle ⁇ is greater than or equal to 0° and less than or equal to 5°.
  • the surface of the outer edge (43) on the side of the negative pressure face (41n) is the curved surface (ws) that is convex on the outer side, and the curved surface (ws) is smoothly connected to the negative pressure face (41n) and is connected to the pressure face (41p) at an angle that is greater than or equal to 85° and less than or equal to 90°. Therefore, an airflow that has reached the vicinity of the outer edge (43) of the blade (40) easily moves along the negative pressure face (41n). Therefore, since it is possible to further suppress separation of a flow at the negative pressure face (41n), it is possible to further suppress loss at the blade (40), and to thus further increase energy efficiency of the cross flow fan (10).
  • a surface of an inner edge (42) on a side of the negative pressure face (41n) is a curved surface that is convex on an outer side, and the curved surface is smoothly connected to the negative pressure face (41n) and is connected to the pressure face (41p) at an angle that is greater than or equal to 85° and less than or equal to 90°. Due to this structure, even in the blow-out region R2 (see Fig. 1 ), it is possible to obtain the same effects as those of the present modification.
  • a wall-mounted indoor unit has been described as the air conditioner indoor unit (1) including the cross flow fan (10), it is not limited thereto, and the cross flow fan (10) may be used in other types of indoor units, such as a floor-mounted type or a ceiling-mounted type.
  • the impeller (20) of the cross flow fan (10) is disposed on the downstream side of the indoor heat exchanger (4) in the direction in which air flows, the impeller (20) may be disposed on an upstream side of the indoor heat exchanger (4) instead.
  • the present disclosure is useful for a cross flow fan blade, a cross flow fan, and an air conditioner indoor unit.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP20870951.9A 2019-09-30 2020-06-01 Pale de ventilateur à flux transversal, ventilateur à flux transversal et unité intérieure de climatiseur Pending EP4027018A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019179027A JP6852768B1 (ja) 2019-09-30 2019-09-30 クロスフローファンの翼、クロスフローファン及び空調室内機
PCT/JP2020/021573 WO2021065079A1 (fr) 2019-09-30 2020-06-01 Pale de ventilateur à flux transversal, ventilateur à flux transversal et unité intérieure de climatiseur

Publications (2)

Publication Number Publication Date
EP4027018A1 true EP4027018A1 (fr) 2022-07-13
EP4027018A4 EP4027018A4 (fr) 2022-11-09

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EP20870951.9A Pending EP4027018A4 (fr) 2019-09-30 2020-06-01 Pale de ventilateur à flux transversal, ventilateur à flux transversal et unité intérieure de climatiseur

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US (1) US11466871B2 (fr)
EP (1) EP4027018A4 (fr)
JP (1) JP6852768B1 (fr)
CN (1) CN114502842B (fr)
AU (1) AU2020359245B2 (fr)
WO (1) WO2021065079A1 (fr)

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CN115234511A (zh) 2022-06-27 2022-10-25 珠海格力电器股份有限公司 贯流风叶、空调器
TWI884701B (zh) * 2024-02-06 2025-05-21 台灣櫻花股份有限公司 抽油煙機的風扇葉輪

Family Cites Families (13)

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Publication number Priority date Publication date Assignee Title
EP1119082A3 (fr) 2000-01-18 2004-05-26 Ushiodenki Kabushiki Kaisha Ventilateur à courant transversal pour un laser à gaz excité par décharge
JP2001274486A (ja) * 2000-01-18 2001-10-05 Ushio Inc 放電励起ガスレーザ装置用クロスフローファン
JP4196346B2 (ja) * 2004-03-25 2008-12-17 三菱電機株式会社 空気調和機
JP4583095B2 (ja) * 2004-07-27 2010-11-17 東芝キヤリア株式会社 クロスフローファン
JP5140986B2 (ja) * 2006-03-15 2013-02-13 株式会社デンソー 遠心式多翼ファン
JP2013079617A (ja) * 2011-10-05 2013-05-02 Hitachi Appliances Inc 空気調和機
JP5143317B1 (ja) * 2012-04-06 2013-02-13 三菱電機株式会社 空気調和装置の室内機
JP6044165B2 (ja) * 2012-08-09 2016-12-14 ダイキン工業株式会社 多翼ファン及びこれを備える空気調和機の室内機
CN104728162B (zh) * 2013-12-24 2017-04-12 珠海格力电器股份有限公司 贯流风叶
JP5825339B2 (ja) 2013-12-27 2015-12-02 ダイキン工業株式会社 クロスフローファンの翼
JP2018084154A (ja) * 2016-11-21 2018-05-31 ダイキン工業株式会社 クロスフロー型の送風機及びそれを備えた空気調和装置の室内ユニット
JP6951428B2 (ja) * 2017-04-10 2021-10-20 シャープ株式会社 遠心ファン、成型用金型および流体送り装置
WO2019012578A1 (fr) * 2017-07-10 2019-01-17 三菱電機株式会社 Unité intérieure pour climatiseur

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CN114502842A (zh) 2022-05-13
AU2020359245B2 (en) 2022-06-16
US20220214052A1 (en) 2022-07-07
JP6852768B1 (ja) 2021-03-31
CN114502842B (zh) 2023-05-05
AU2020359245A1 (en) 2022-04-07
EP4027018A4 (fr) 2022-11-09
JP2021055603A (ja) 2021-04-08
WO2021065079A1 (fr) 2021-04-08
US11466871B2 (en) 2022-10-11

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